Miniature bulletin printer



Aug. 17, 1965 E. E. KLEINSCHMIDT ETAL MINIATURE BULLETIN PRINTER SSheets-Sheet 1 Filed Oct. 19, 1961 INVENTORS Edward E. Kleinschmiclr Wilburn F Bradbury Wy 7W Attorneys Aug. 17, 1965 E. E. KLEINSCHMIDT ETAL 3,201,514

MINIATURE BULLETIN PRINTER 5 Sheets-Sheet 2 Filed Oct. 19, 1961 INVENTORS Edward E. Kleinschmidi Wilburn F Bradbury REVS 5 Sheets-Sheet 3 INVENTORS Edward E. Kle'inschmidt 7L 5 Attorneys Aug. 17, 1965 E. E. KLEINSCHMIDT ETAL MINIATURE BULLETIN PRINTER Filed Oct. 19. 1961 BY Wilburn FBrodbury Aug. 17, 1965 E. E. KLEINSCHMIDT ETAL 0 4 MINIATURE BULLETIN PRINTER Filed 001:. 19. 1961 5 Sheets-Sheet 4 Hull LLL Ill| INVENTORS Edward E. Kleinschmidt By Wilburn F Bradbury Attorneys United States Patent 3,201,514 MINEATURE BULLETIN PRINTER Edward E. Kleinschmidt, Miami Beach, Fla, and Wilhurn F. Bradbury, Northbroolr, llL, assignors t0 SCM Corporation, New York, N.Y., a corporation of New York Filed Oct. 19, 1961, Ser. No. 146,105 50 Claims. (Cl. 178-33) The present invention relates to apparatus for receiving and recording coded signals and more particularly to a small compact bulletin printing apparatus exemplified in the following disclosure by what is commonly known to the telegraph industry as a printer. 7

Apparatus for receiving coded signals and automatically transforming them into recorded typographical characters for immediate reading .are well known in the art and usually consist of components such as a typewheel, print hammer and mechanism to select .a specific character .and to cause relative movement between the typewheel and print hammer, a reversible inked ribbon mechanism and a carrier and feed for the paper on which the message is printed.

In previously known equipment of this type, most of the above-mentioned components are located on the front side of the paper, making it most difficult, if not impossible, to read the printed message the instant it is being typed. Also, many of the previously known machines employ costly helical shafts and gears and other complex devices in the mechanism for relatively positioning the printing components, necessitating constant adjusting and servicing.

The present invention includes similar basic components, such as the typewheel, print hammer, etc., however the printwheel is located behind the paper with the print hammer and ink ribbon being in front and other structure is designed so as to permit complete visibility of the simplifies the organization of printing controls and function controls and also makes possible the addition of more function bars than was heretofore practical in-previously known designs. t

Accordingly, a primary object of this'invention resides in the provision of novel printer construction permitting miniaturization.

A further object resides in the provision of a novel miniature printer utilizing selector mechanism in which code members for controlling printing of desired characters are in a physically separate assembly from an a sem'bly of code members which determine and control machine functions. In conjunction with this object it is a further object to provide compactness of the machine mechanism by arrangement of the power operating and selecting mechanism so a major portion is spaced beside and parallel with the drive motor, the print selector code member assembly being arranged in a cylindrical fashion perpendicular to a selectively positioned type selecting vision of novel mechanism for operating the coded mem- 3,201,514 Patented Aug. 17, 1965 bers of a stop bar assembly in which all coded members are placed in a common home position, e.g., all coded members in mark position prior to receipt of each code signal combination and only those members corresponding to a space designation in the coded signal combination will then be shifted, the remainder being retained in mar position by energized solenoids. This arrangement permits faster operation, use of smaller solenoids and lower current because the solenoids only hold the 'coded members in position, they are not required to exert the large force to attract and shift the coded members.

The foregoing object constitutes a novel generic concept which is utilized in a circular arrangement of stop bars (the print stop bars) as well as a linear arrangement of operating bars (the function operating bars).

A stillfurther object resides in the novel combination of the foregoing selecting mechanism with a typebar page printer.

Still another object resides in .a novel stop arm assembly for use with a circular stop bar cage assembly using .a simple rebound detent leaf to assure accurate angular positional location of a rotatable'type character selecting member.

A further object resides in providing a novel cable rigging shift mechanism for accomplishing interoperational shift of the typewheel to enable selection of different characters from identical positions on alternative rows on the typewheel without affecting character spacing of the re cording operation.

Another object resides in the provision of a novel printer with components disposed to allow the recorded message to be read insofaras it has been recorded as soon as the recording of such character has been completed.

Still another object resides in the provision of a novel printing device having a synchronously traversing print wheel and print hammer, an ink ribbon passing between the print hammer and typewheel wherein a message is printed on a page disposed between the typewheel and the print hammer on a the side of the page adjacent the hammer.

A further object resides win the provision of apage printing device with novel synchronized mechanism capable of automatically returning the typewheel and print hammer to one side and simultaneously indexing the paper to permit printing of successive lines of a message.

Another object of this invention resides in the provision of a telegraphic page printer having a traversing print hammer with novel mechanism for blocking print hammer operation responsive to a received function signal.

Further novel features and other objects of this invention will become apparent from the following detailed description, discussion and the appended claims taken in conjunction with the accompanying drawings showing a preferred structure and embdiment, in which:

FIGURE 1 is a perspective view of an exemplary typewheel page printer made in accord with the present invention and illustrates the relative positions of the various components such as ink ribbon,-print wheel, print hammer, print selection stop bars, function operating bars, etc., the frontal framing of the machine being deleted for clarity;

FIGURE 2 is a detail perspective View of the positive cyclic clutch mechanism which can be seen below the typewheel in FIGURE 1 and which controls the camshaft cycles of rotation, the length being exaggerated for purposes of clarity in illustration; 7

FIGURE 3 is a further detail view of the positive clutch mechanism shown in FIGURE 2 and illustrates the manner in which the sliding clutch member is keyed to the camshaft;

FIGURE 4 is a view of the slip clutch mechanism located in the drive train between the camshaft and the rotatable character selecting stop arm typewheel shaft;

FIGURE 5 is a perspective view looking at the rear of the machine and shows the circular and the linear coded members, the associated stop and function bars, the code cage and other relative parts;

FIGURE 6 is a detail view showing the rear of the code cage and related components and illustrates relationships and connections between the code bars, code rings, print stop bars, function bars and operating solenoids;

FIGURE 7 is a skeleton perspective view showing components of a traversing typebar opearting mechanism which can be used in lieu of the typewheel and print hammer mechanism of FIGURE 5, the details of such a traversing typebar arrangement being disclosed in aprior Kleinschmidt Patent No. 2,773,931;

FIGURE 8 is a right side view of the printer and primarily illustrates mechanical features relating to machine functions;

FIGURE 9 is a detail top view of a modified function bar and hail assembly illustrating component positions an instant before the function bar falls into its operating position;

FIGURE 10 is an additional detail view of the modified function bar arrangement similar to FIGURE 9 excepting it shows the function bar in a selected position ready to be engaged by the shifting bail;

FIGURE 11 is a perspective view, partially cut away showing the resetting mechanism for the stop bars and the function operating bars;

FIGURE 12 is a detail section view of a modified solenoid linkage connection, also shown in FIGURE 11;

FIGURE 13 is a schematic side view showing the print hammer actuating mechanismand its relationship to the function operating bars which are provided with mechanism to accomplish print hammer blocking;

FIGURE 14 is a detail top view of the Letters-Figures shifting mechanism;

FIGURE 15 is a perspective drawing of the mechanism in FIGURE 8 providing additional details of the Letters-Figures shifting mechanism;

FIGURE 16 is a machine cycle, timing chart; and

FIGURE 17 is a skeletonized perspective showing the camshaft and cams and illustrates the general operational relationship between the print wheel, the square shaft, the stop arm and the character selecting mechanism.

As seen in FIGURE 1, the exemplary printer 2G in corporating the present invention is a typewheel page printer consisting of a typewheel 22 and print hammer which are letterspaced across a page with the typewheel behind the page. The printing hammer 24 is located in front of the paper 25 and is letter-spaced in register with the typewheel. Printing is effected by striking the hammer against an inked ribbon between the hammer and the paper and forcing the paper against the typewheel. The typewheel 24 is mounted on and rotated by a square shaft 26 through a friction drive (FIGURES 4 and 17) being stopped in a selected character position when a selected stop bar 28 is moved into the path of a stop arm 30 (FIGURES 5 and 17) which is drive connected to the square shaft 26.

In the present invention, code signal combinations of parallel signal form are used, although it is to be understood that such telegraphic signals can be received from a line in series and then converted to parallel form to operate the machine. Print selecting operations are effected through the positioning of five permutation code disks and concurrent positioning of five lineally mounted permutation code bars enable carriage return, Letters- Figures shift and other printer control functions. Although line feed per se is not included as a function of the exemplary embodiment, it is to be understood that such a well known separate machine function as well as others known to those skilled in the art, can be easily included if desired.

Referring to FIGURES 1, 5 and 11, five permutation 4 code disks 31 and a stop bar resetting cam disk 32 are pivotally mounted about the axis of a stop arm shaft 34 which derives rotation by means of a worm 36 attached to shaft 34 and meshed with a worm gear 38 which is drive connected to the square shaft 26. Mounted in a cage 49 surrounding the code disks 31 and ad acent the periphery of the code disks and at right angles thereto are twenty-six stop bars 28, all of which are held slightly above the edges of the code disks 31 by virtue of their respective engagements with the outermost surfaces of cam rises on the periphery of the cam disk 32. The stop bars 28 are resiliently urged inwardly to such position, being spring loaded by a circular coil spring 42 circumscribing the code bar cage 40. The stop bars 28 have suitable step formations (not shown) which cooperate with the cage end plates to prevent endwise shifting of the bars. The cage end plates are rigidly secured to each other by bolts which also fasten the cage 40 to the machine frame.

Code disks 31 have square cut notches 44 in their peripheries disposed in a predetermined arrangement so that, when the code disks 31 are selectively rotated n one direction, a selected group of the notches 44 will fall under one selected stop bar 28 forming a trough. This happens once each time a selection is made and the selected stop bar 28 will then be forced nwardly into this trough by spring 42. The angular posit ons of these stop bars 28 correspond to the angular positions of the associated type characters on the typewheel 22.

Five vertically mounted function code bars 46 and a function resetting cam bar 48 (see FIGURE 8) are linked, as will be hereinafter described, to corresponding code disks 31 and cam disk 32, respectively, for conjoint actuation with associated disks. These code bars 46 are shifted by proper signals to select a machine function, i.e., carriage return and line feed, Letters shift, Figures shift, signal bell, etc., and operate in a manner similar to that of the code disks 31. Disposed horizontally across the notched code bars 46 and the resetting cam bar 48 (at right angles thereto) are a plurality of function operating bars 50 (six being shown) which, upon being shifted, cause the selected functions to be performed. Shown in FIGURE 13, additional function operating bars 50, added in phantom lines can be used for various other functions such as to ring a signal bell, to start an answering or return signal device, for controlling other allied equipment, etc. Add t onal function operating bars 50 can be added as additional functions are desired, thirty-two separate functional operations being possible with a five unit code.

The function operating bars 50 lie across the function code bars 46 at right angles to them and thus, when the code bars 46 have been set by the five selector solenoids 52 (FIGURE 5), for a desired function, the selected operating bar 50 will enter into the aligned permutation notches in the bars 46. When an operating bar 50 shifts, a rectangular cut-out 54 (FIGURE 1), in the side of the selected operating bar 5%), shifts into the path of movement of a reciprocally mounted function bail 56. The function bail 56 (see FIGURE 8) is cyclically reciprocated by a bell crank 58 having a follower 69 which rides the surface of a bail operating cam 62. As bail 56 is shifted toward the rear of the machine, its leading edge 57 will engage the edge of the cut-out 54 in the selected function operating bar 50 and will force that selected function operating bar horizontally toward the rear of the machine against the bias of a spring 63, such movement being enabled by its forked end sliding in an associated notch on the shank of a vertical pivot shaft 64. Through connecting linkages such as the bell crank. and lever arrangement shown in FIGURES 14 and 15 (to be described later) the desired function will be accomplished.

It is necessary to block the printing when most funcnous are performed because the yp wheel 22 will not,

usually. arrest during these cycles. Accordingly, the function operating bars 50 are each provided with a lug 66 (FIGURE 13) which extends behind a print blocking lever 68 which, upon a function operating shift of any of the operating bars 50, will be moved into the path of a component of the printing mechanism to block printing operation. Print blocking will be explained in more detail hereinafter.

Receipt of each code signal combination by the printer starts an operational cycle which automatically terminates upon completion of one complete cycle. Referring to FIGURE 1, operational power for the printing operations and to accomplish the desired machine functions is derived from a constant speed electric motor 70 located at the rear of the printer 20 on the opposite side from the described code member cage assembly 40. The motor shaft 72 is horizontal and projects toward the front of the printer, carrying a worm 74 on its projected end.

When the machine is conditioned to receive and record signals, the motor 70 will be continually'rotating and thus a further feature necessary to operation of the printer is the mechanical start-stop mechanism. Extending laterally and completely across the machine is a rotatably mounted shaft 76 which carries all of the operating cams and a clutch 78, details of which are shown in FIGURES L2 and 3.

Freely rotatably mounted on the camshaft 76, as the input member of clutch 78, is a Worm wheel 80 which meshes with and is driven by the worm 74 on the motor shaft 72. Worm Wheel 80 has small clutch teeth 82 on one side which can engage teeth in a mating clutch face 84 on the side of an axially slidable clutch member 86. The slidable member 86 (see FIGURE 3) is disposed on and keyed to the camshaft 76 by a cross key 88 whose ends fit in a slot 90 cut across the end of the slidable member 86. Key 88 projects completely through shaft '76. By such arrangement, the slidable clutch member 86 may slide back and forth in a guided motion although it is non-rotatable relativeto shaft 76- The slidable clutch member 86 is biased by a coil spring 12 toward engagement with the teeth 82 on worm wheel 80 and is normally held out of such engagement by a clutch finger 94 on the slidable member which engages and is latched by the end of armature 96 of a start solenoid 98. When the winding of solenoid 98 is energized by a start signal, its armature 96 is pulled downwardly and away from latching engagement with the clutch finger 94, whereupon the slidable clutch member 86 is moved under spring bias into engagement with the worm wheel clutch face 84 and the camshaft 76 will start its 360 cycle of rotation. Upon completion of one revolution of the cam shaft 76, clutch finger 94 again engages the upper end of the solenoid armature 96, which in the meantime has been restored by a spring 1110 upon de-energization of the solenoid 98. Upon such engagement, the slidable clutch member 86 is cammed away from engagement with its mating worm wheel teeth 32 because of the sloping leading edge 102 of clutch finger 96, disconnecting the motor drive, whereupon, camshaft 76 ceases rotation.

On the right hand end of the clutch 78 and working in conjunction with clutch actuation is an anti-bounce device consisting of a leaf spring 164 cooperating with a step cam 106. When clutch finger 94 hits the solenoid armature 96, the stopping of shaft 76 is rather abrupt and considerable bouncing or camshaft backlash would normally be experienced. However, an instant before the base of slope 102 on clutch finger 94 bottoms against the end of the solenoid armature 96, the tip of leaf spring 104 falls off the step 107- of cam 106 to interlock cam step 107 and leaf spring 104 and obviate any tendency to bounce.

Partially visible in FIGURE 1, at the extreme left side of the printer 20, is a second clutch 168 of-the slip coupling type (see FIGURES 4 and 17) consisting of a large gear 110 rotatably mounted on camshaft 76 and frictionally driven by rotation of camshaft 76 through the medium of two oiled felt disks 112 and 114 and two Washers 116 and 118, the combination being pressed together with the felt disks bearing against the gear 110 by the force of a compression spring 120. The slip clutch 108 is a necessary component due to the fact that camshaft 76 at certain times during an operating cycle must be in motion even though the print wheel 22 and its associated selecting mechanism are stopped at the selected printing position. The square shaft 26, extending across the machine above and parallel with the camshaft 76, has a cylindrical left hand end projecting through the left side of the machine frame 126 and nonrotatably carries a small gear 128 which meshes with the large gear 116 in the slip clutch. Gear 128 is slightly more than one half the diameter of gear 110 and the relative number 'of gear teeth provide a step-up speed ratio of 1.66: 1. Because of this step-up ratio, the square shaft 26 will rotate very nearly twice as fast as does the camshaft 76. The increase in speed of rotation 'of the square shaft is necessary to insure completion of character selection in the event the stop arm 36 has to make its maximum arc oftravel during an operational cycle. This will be explained in further detail hereinafter.

On and near the right hand end of the camshaft 76, located inside the machine frame, are two more cams 130 and 132. Cam 130 will operate the print hammer 24 (FIGURE 13) and cam 132 operates the restoring (resetting) mechanism for the permutation code disks 31, the cam disk 32, the code bars 46 and cam bar 48 (FIGURE 11). The print cam 130 is formed with a deep and abrupt drop-off sector 134, where the printing operation is performed, followed by an easy rise high side 136 which by means of a follower roller 140 on cam follower lever 142, respectively permit the lever 142 to turn under the urging of a'spring 144 and then to gradually reload the spring 144 without overloading the drive motor 70.

The printing hammer 24 is slidably mounted on an oscillatable flat shaft 146 extending across the front of the printer, and mounted in bearings in the machine frame side plates. The hammer slides easily on the flat shaft under the control of a cable 148 which is attached by a suitable anchor clip to the rear face of the print hammer base block 150. Cable 148 letterspaces and returns the hammer 24 across the paper 25, synchronized and in alignment with the print wheel 22 (FIGURE 1). A lever 152 shown in FIGURES 13 and 17, rigidly fastened on one end of the fiat shaft 146, engages one end-154 of the print cam follower lever 142 and the force of abiasing spring 156 secured to finger 158 of the print lever 152 tends to keep the two levers 152 and 142 together. When cam follower 1461 on follower lever 142 falls into the fast drop-off recess 134 of print cam 1341, a blow is imparted to the print lever 152 which pivots the fiat shaft 146, causing the hammer 24 to strike the ribbon and paper against the typewheel 22.

As indicated in the timing chart of FIGURE 16, the spacing operation and the character selection occur during a period of the operational cycle proceeding the print action of the hammer. The mechanism and operation by'which spacing is accomplished inter-relates the print hammer and typewheel and results in their synchronized spacing movements and will now be described followed by a description of the mechanism and operation of the code members with selection of characters to be printed and/ or functions to be accomplished.

Letter spacing of the typewheel 22 and the print hammer 24 across the page and their return to the left margin is accomplished as follows:

At the right hand side of the printer 20, toward the back of FIGURE 1, a pulley 161 having two parallel grooves of equal diameter in its periphery, is mounted for rotation on a pulley stud 162 fixed in a side member of the machine frame. Rigidly fastened on the inner face of the pulley 160 is a ratchet wheel 164 (see FIG- URE 8) containing a number of teeth greater than the number of characters to be recorded on a line. This ratchet 164 is turned one tooth, each time the printer cam shaft cycles, by a space pawl 166 pivotally carried on the end of a cam follower lever 168 which is pivoted on a post 170 and carries a cam follower 172 rolling on the previously described function bail operating cam 62 located on the camshaft 76.

At the left hand side of the printer 20, are two clockspring drums (one 176 being shown schematically in FIGURE 17) with annular grooves for the thin wire cables 148 and 174. One of the spring drums 176 is wound with one end of the cable 174 which passes over an idler pulley 178 to a horizontal stretch and over a second idler pulley 180 at the opposite side of the printer where the other end of cable 174 is wound on the inside groove of, and is secured to, cable pulley 160. Between the two idler pulleys 173 and 1811 cable 174 is attached by clip 184 to the typewheel carriage 182 which is slidably mounted on a horizontal rod 186. The hub 188 of typewheel 22 may be integral or separable from the typewheel 22 but in any event it contains a square hole which permits the typewheel to be axially slidable along the square shaft 26 yet at the same time the type- Wheel 22 will rotate with the square shaft. The typewheel carriage 182 includes a yoke with two fork shaped arms 190 to embrace the typewheel 22 and fit over the hub 188. Thus, the carriage position will determine the axial position of typewheel 22 yet permit typewheel rotation as dictated by rotation of the square shaft.

The other cable 148 is wound on its spring drum (not shown), passes over an idler pulley (not shown) at the left side of FIGURE 1, along a stretch parallel with and adjacent to the flat print hammer shaft 146, to and over a second idler pulley 192, thence to and around the outer groove in large pulley 160, being suitably secured to the large pulley. As has been described, the cable 148 is secured by an anchor clip at an appropriate point along its horizontal stretch to the base block 150 of the print hammer.

When the ratchet wheel 164 is turned an angular increment of one tooth space, the two distinct runs of cables 148 and 174 are each simultaneously wound the distance of one letter space on the double groove cable pulley 161) and are unwound one letter space distance from each of the left side spring drums. The pulling of cables 148 and 174 from the spring drums winds the clocksprings in the two drums and the typewheel 22 and the print hammer 24 are thus stepped across the paper in unison.

Carriage return, line feed and Figures and Letters shift, being function operations, will be described following a description of the mechanism for selecting and resetting the code members.

Code mechanism and operation Referring primarily to FIGURE 11, but also with reference to FIGURES and 17, the aforenoted resetting cam 132, on cam shaft 76 provides the power for restoring the code disks 31 and the code bars 46 and, through the medium of cam disk 32 and cam bar 48, also resets any selected one of stop bars 28 and function bars 511.

Cam 132 is an axial cam and is engaged by two cam followers 194 and 196 both of which are pivotally carried on a shaft 199. Cam follower 194 cams all of the selecting solenoid armatures 198 to the normal or operated position and thereby restores all of the code disks 31 and code bars 46 to their normal position. The other cam follower 196, is connected to and operates the stop bar restoring cam disk 32 which has twenty-six camming teeth or projections 2119 around its periphery, one for each of the twenty-six stop bars 23.

As the cam 132 rotates, cam follower lever 194 pivots on shaft 199 as the cam follower riclcs up the rise 201 of earn 132, causing a bias spring 292 to be flexed. When a selected stop bar 28 is down in an aligned row of square notches 44 of code disks 31, the code disks 31 are locked against movement by respective levers 206, each of which has a depending arm which is connected to an armature 197 of an associated solenoid 52. Therefore, the aforedescribed spring 202, which is anchored to a bail 208 which in turn is pivotally supported on the shaft 199 and abuts the ends 207 of armatures 193, cannot pivot the bail 208 until the cam disk 32 is operated to restore the previously selected stop bar 28. However, restoring will occur an instant before the first cam follower 194 falls off the camming rise 201, because the second follower 196 will have begun its ride up the camming rise 201. As it does so, it causes cam disk 32 to rotate and through a specific tooth 200 corresponding to the selected stop bar 28, will cam the stop bar 28 out of the aligned code disk notches, thus freeing the code disks 31 to be moved. The instant the code disks 31 are free to move, spring 2112 snaps the bail 208 against the ends 207 of armatures 198 moving them all back to the normal or operated positions against the bias of all five of the armature springs 210.

It will be seen that the linkage connection of the solenoid armatures 198 to levers 2% as shown in FIG- URES 11 and 12 is an alternate arrangement as compared to the linkage connection shown in FIGURE 5. In the alternate arrangement, bail 203 hits pivoted connector blocks 211 (shown in FIGURE 11), one on each armature, each of which in turn pushes against a spring 213 which abuts a washer 215. On the opposite side of washer 215 is the normal armature spring 210 which, being the lighter of the two springs, is overcome first as armature 198 moves inward. When armature 198. moves sufficiently to bottom in its core 217, bail 208 can still continue to rotate counterclockwise, causing pivoted connector block 211 to slide on end 219 of armature 193, finally overcoming spring 213 partially. In this alternate construction, a more efficient connection between armature 198 and core 217 is achieved than is present with the construction shown in FIGURE 5.

Operating in conjunction with the reset cam follower 196, and being permanently attached to its end 212 by a rivet 214 is a lever 216. When arm 218 of cam follower 11% rotates cam disk 32 to reset the selected stop bar 28, the lever 216, being rigidly attached thereto, simultaneously moves the aforedescribed function cam bar 48 upward and its teeth 233 cam any selected one of function operating bars 51) out of the notches in function code bars 46, whereupon the spring 63 associated with that function operating bar 51 will return it to its neutral position.

With the printer in the stop or idle position, that is, with clutch teeth 84 and slidable member 86 apart or open (FIGURE 3), selector solenoid armatures 198 all pressed in against the bottoms of solenoids 52, stop bars 28 and function operating bars 50 all camrned away from the code disks 31 and the code bars 46 and with the function bail 56 and the space pawl 166 in the retracted position the operational sequence of a cycle, where printing occurs using as an example receipt of the code signal for the letter E, proceeds as follows:

The printer receives a signal corresponding to the letter E, which is a closed circuit to only one of the selecting solenoids 52. Simultaneously with the recept1on of this signal there is an electric pulse given to the starting solenoid 93 which permits the clutch 78 to engage and starts rotation of camshaft 76. Immediately thereafter, the cam follower lever 194, associated with ball 208, which is holding all of the selecting solenoid 59 armatures 198 in their normal (operated) positions, drops off the cam 132 and all of the solenoid armatures 198, except the one associated with the energized solenoid 52 will be released. The number 2, 3, 4 and 5 code disks 31 will turn under the bias force of the solenoid springs 210 and a trough of aligned notches 44 is created directly beneath the E stop bar 2?. Immediately thereafter the cam follower lever 196 associated with the cam disk 32 drops off the cam 132 and cam follower lever arm 218 rotates the cam disk 32 to the position which permits all of the stop bars 23 to rest on the edges of the code disks 31. Since, as has been just described, the code disk notches 44 are now aligned to form a trough beneath the E stop bar, the E stop bar 28 drops into the trough under resilient bias of the coil spring 42. Stop arm 30 (FIGURE 5) which started to rotate upon start of rotation of the camshaft '76 (from frictional motivation derived through slip clutch 108, square shaft 26 and gears 36, 38) continues to rotate until it engages the dropped end of and is stopped by the selected E stop bar 28. This also stops the rotation of square shaft 26 at an angular position where the E character on the typewheel 22 is in the print position behind paper 25 and in line with the print hammer 24 and the mechanism is ready for the print operation.

As previously described, the increased speed of rotation of the stop arm 30 with respect to that of camshaft 76 is necessary to insure completion of selection of a character if the stop arm 226 has to rotate through its maximum .arc. Since part of the cyclic time period is used up at the start of the cycle to set the code in the code disks 31 and to release the stop bars 28 and because a further part of the cycle will be required at the end of the cycle to enable printing and restoring, just a little more than half a cycle is available to set the typewheel 22. A certain amount of slippage occurs (due to slip clutch 108) before the square shaft 26, shaft 34 and stop arm 30 reach speed. For such reasons, additional speed over and above the minimum required for selection has been provided.

Provision has been made to prevent rebound of the stop arm 30 when it strikes a selected stop bar 28. In FIG- URES 5 and 6, a spring finger 228 fastened on the end of the stop arm 30 is sprung out as an end lip on its front edge rides over the end of the selected stop bar 28. Then, when the stop arm 30 hits and is stopped by the stop bar 28, the spring finger 228 springs in and its back edge latches the stop arm 30 to the stop bar 28 by straddling the selected stop bar. All rebounding tendencies of the stop arm 30 are positively eliminated by this convenient structural arrangement.

As represented in the timing chart of FIGURE 16, subsequent to the start of rotation of camshaft 76, the space pawl 166 on cam follower arm 168 (FIGURE 8) is driven into the ratchet 164 and spacing of the typewheel 22 and print hammer 24 takes place approximately 90 before print action occurs.

Immediately after the E stop bar 28 has dropped into the aligned code disk notches 44, the E signal (a closed circuit to a solenoid 2193) can be discontinued and the selection is locked in until the end of the cycle.

' About midway into the cycle the space pawl 166 has reached the top of its travel and starts its reverse movement to be restored. The space ratchet wheel 164 will be latched in this advanced position by a carriage return pawl 204, to be later described. Also, at this approximate mid-point of the cycle, a slight lowering of the print cam follower 140(FIGURE 13) on the print cam 130 occurs for a reason to be hereinafter explained. As the cycle proceeds, the space pawl 166 continues to be restored and at about three-quarters of the way through the cycle the print cam follower 146B abruptly falls into the deep recess 134 of the print cam 130 causing end 154 19' of the print cam follower lever 142to strike print lever 152 sharply downward, which actuates the hammer 24 and thereby causes the selected character to be printed on the paper 25.

Following the printing action, the restoring bail 208 for the selector solenoids 52 is operated as was described previously. Following closely behind the operation of the restoring bail 208, the cam follower 196 for cam disk 32 rotates the cam disk 32 which in turn resets any selected stop bar 28 as was previously described.

The final action in the operation sequence is'the disengagement of the space pawl 166 from the ratchet wheel 164, which occurs in the final instant of the return motion of the space pawl 166. As the space pawl levers cam follower 172 rides the high part of cam 62, the cam follower lever 168 is rotated clockwise, around pivot point 170 (see FIGURE 8) and as the space pawl 166 moves downward, an integral leg 232 hits a fixed stop 234 causing the space pawl 166 to pivot counterclockwise. This movement pulls toothed end 236 out of engagement with ratchet wheel 164. An instant later the positive clutch 78 on camshaft 76 is disengaged, and rotation of the camshaft 76 is stopped which also stops rotation of the square shaft 26 putting the machine in its neutral or idle condition. During the nexticycle as the cam follower 172 rides the low point of the cam 62, lever 168 rotates counterclockwise raising the space pawl 166 attached to the opposite end and, as the toothed end 232 of space pawl 166 raises up from its stop 234, the space pawl 166 will pivot in a clockwise direction under bias of pawl spring 238. When it does so, toothed end 236 again engages the ratchet wheel 164.

Before proceeding with a description of the operational sequence for a machine function, the mechanisms which accomplish carriage return, line feed and Letters and Figures shift will be described.

Carriage returnline feed Since the typewheel 22 and the print hammer 24 traverse across the page in conjunction with each other the function of carriage return will include simultaneous return of the typewheel and the print hammer.

Associated with the letter spacing ratchet wheel 164 is the previously mentioned carriage. return pawl 204 which engages the ratchet wheel 164 and acts as a detent to prevent its turning backward after each letter space operation. An extension arm 240 of the carriage return pawl 204 (as seen in FIGURE 8) lies adjacent the carriage return function operating bar 50a and a knob-like upper projection 242 on this bar 50a will strike theunder side of the pawl extension arm 240 whenever the specific carriage return function operating bar 50a is pushed to the right by movement of the function bail 56. The carriage return pawl 204 will be moved clockwise, away from engagement with the ratchet wheel 164, to free the ratchet wheel and its associated double pulley allowing both of the spring drums 176 (one not shown) to wind both cables 148 and 174 and pull the print hammer 24 and type wheel 22 to the left-hand margin. When tooth 244 of the carriage return pawl 204 is moved to be disengaged from the ratchet wheel 164, the return pawl 204 will become latched in retract position by an integral projection 246 which moves past and is latched behind an end 247 of a pivoted latch lever 248, the lever being urged clockwise by a spring 249.

To unlatch the return pawl 204 at start of line position, a stud 167, fastened on the side of the ratchet wheel 1 64, will strike the latch lever 248 when the typewheel 22 has reached the start of the line position, and will shift the latch lever 248 counterclockwise to unlatch the pawl 204 which is then pulled upward by its spring 205 to again engage the teeth of the ratchet wheel 164.

The line space (paper feed) mechanism is seen in FIG- URES 1 and 5 and is effected by the use of two rubber rollers 22% and 221 pressing against the paper guide 222 (see FIGURE 5) with the paper in between. By turning the rollers 220 and 221 a peripheral distance of one line space (automatically or manually by means of a knob 223) the paper 25 will be advanced by that distance. At the end of the shaft 224 to which the rollers 22% and 221 are attached is a ratchet 225 (FIGURE 8) which is engaged by a pawl roller 226 in the end of a pawl lever 227, said pawl lever 227 being urged clockwise by a spring 228 and pivotally connected to the carriage return function bar a through a bell crank 229 and a link 230. As seen in FIGURE 1, the link 230 interlocks between two tabs 231 on the carriage return function bar 50a.

When a carriage return signal is received by the printer, the function bail 56 is forced to positively move to the rear, catching in the cut-out 54 in the inside edge of the carriage return function operating bar 50:: and therefore carriage return function operating bar 50a will be forced to move to the rear. This movement of operating bar Sila pulls the link 239 (which is locked thereto) with it and link 230, being attached to the bell crank 229, rotates the bell crank in a counterclockwise direction causing line feed pawl lever 227 to move downward which in turn causes its roller pawl 226 to engage a tooth on the ratchet 225 and rotate the ratchet with the attached paper feed shaft 224 to index the paper 25 one line space. Thus, the carriage return function and the line feed function in the disclosed mechanism are operated by the same signal, obviating the need for a separate line feed signal. Any line feed signals which might inadvertently be sent to the printer will not result in a line feed function, they merely cause a letter space operation inasmuch as the letter spacing mechanism operates regardless of what signal is sent and inasmuch as no carriage return signal was received. Blank signals (signals with a starting pulse only) likewise will merely letter-space the machine without printing.

Letters and Figures shift The Letters and Figures shift mechanism utilizes a portion of the cable rigging of the character spacing mechanism.

Idler pulley 180 which directs the typewheel cable 174 to the large cable puley 16% has its axis disposed perpendicular to that of the cable pulley 160 and is mounted for movement in a right and left direction, that is, in line with the direction of the main stretch of the cable 174. When the typewheel 22 is in position to print alphabetical characters (Letters), its right-hand row of type 250 is registered behind the printing hammer 24. When it is desired to print numerical. characters (Figures), it is only necessary to move the idler or shift pulley 188 far enough to the right to reposition cable 174 to bring the left-hand row of characters 252 of the typewheel 22 into register behind the print hammer 24, it being understood that the printing hammer 24 does not move as a result of this Figures and Letters shift of the typewheel. The shifting of the idler pulley 180 is performed by operation of the Figures function operating bar Silo in the following manner:

As shown in FIGURES 8, l4 and 15, the idler pulley 189 is rotatably carried on one arm 254 of a triple arm lever 256 pivotally mounted on vertical pivot on the machine frame. The other two arms of lever 256 have bent depending fingers 258 and 260 for purposes to become apparent. An upright post 262 on the machine frame pivotally supports two bridge shaped lever members 264 and 266, lever 264- being the Figures shift lever and lever 265 being Letters trip lever.

A projecting 'arm 268 on the lower end of the Figures shift lever 264 is interlocked with ears 2'70 adjacent the forked end of the Figures function operating bar She and when the Figures function operating bar 500 is moved to the rear of printer 20 by function bail 56, after receipt of a Figures signal, the shift lever 264 rotates counterclockwise on pivot 262. Upper arm 262 of shift lever 264 moves counterclockwise and abuts the depending finger 253 of pulley lever 2536, making pulley lever 256 rotate clockwise. This action causes the other depending finger projection Ztii) of pulley lever 25% to move past a latching end 274 of the Letters trip lever 266, and results in latching of the pulley lever 256 in Figures position. When the pulley lever 2S6 pivots and shifts the pulley 1S9 clockwise, it pulls on cable 174 just enough to shift the typewhcel 22 to the right on square shaft 26 to ready the machine to print on the typewheel Figures row 252.

To return back to a Letters printing condition, a Letters signal must be received by the printer. In the meantime, of course, the Figures function operating bar 5110 will be restored back to its inoperative position, causing the Figures shift lever 264 to pivot until its upper end 272 is clear of the depending finger 258 on pulley lever 255. Thereafter, upon receipt of 2. Letters signal, the Letters function operating bar 5% will be selected to shift into operating position, and it is then moved to the rear by the function bail 56. In so doing the Letters trip lever 256, being linked with the Letters function operating bar 5% in the same manner as the Figures shifting lever 264 is linked with the Figures function operating bar S-llc, will be pivoted counterclockwise. As the Letters tripping lever 266 pivots counterclockwise, the upper latch arm 274 will move away from blocking engagement with the pulley lever finger projection 260, permitting the spring loaded cable 174 to pull the pulley lever 256 counterclockwise until its other depending finger projection 258 is again abutting against the upper arm 272 of the Figures shift lever 2&4. The Letters function operating bar 5911 is then restored to its inoperative or normal position and the machine is ready to commence printing in the Letters condition.

The operational sequence for a function is as follows, using carriage return as the exemplary function:

A carriage return signal is received and results in a completed circuit to a selector solenoid 52 (different from that for letter E) and again a start pulse is sent to the starting solenoid 93. The cycle proceeds as has been previously described for a printing cycle but instead of a stop bar 28 moving into a trough of notches 44 on the code disks 31, the carriage return function operating bar 59a moves into a function code bar notch trough, all of the bars 5% being resiliently biased in such direction by the angularly canted springs 63. The function bail 56 (FIGURE 8) which starts to move at the start of a cycle, engages the edge of cut-out 54 in the carriage return function operating bar 59a (FIGURE 1) carrying the bar Sfla rearwardly. In doing so, the print blocking lever 53 (see FIGURE 13) is moved clockwise by a small lug 66 attached to the top of function bar Sila. Lug 66 is designed to move print blocking lever 68 in a clockwise direction only until its hooked upper end 289 is shifted to a position directly above a bent extension finger 2.32 below the follower Ml) on print cam follower lever 142. Subsequent to the part of a cycle when the print blocking lever 68 is shifted to its blocking position, the print cam follower M 9 moves onto the aforementioned slightly lowered cam surface 284- of the print cam 13%}, causing the follower lever 142 to rotate counterclockwise a slight distance suflicicnt to raise the extension finger 282 into engagement under the hooked end 280 of the print blocking lever 68. the print cam follower lever 142 and. prevents its further move rent. Being now blocked, its operating end 154 cannot actuate the print lever 142, and the print hammer 24 is rendered inoperative. This blocking operation is necessary to permit carriage return and line feed operations to be completed and the carriage return function operating bar 59:: to be restored to its starting position without print movement of hammer 24.

All of these function operations must terminate before This engagement latches- 13 the operating linkage for the print hammer 24 can be released. At the end of the cycle the print cam follower 140 rides up to the high side 136 of cam 13!} and as this movement occurs, the print follower lever extension finger 282 is lowered, automatically disengaging from and releasing the hooked end 280 of print blocking lever 68. The instant that lever 68 is released, its biasing spring 286 moves the lever 68 counterclockwise to its normal unblocking position.

A print blocking action will occur during any cycle when a function operating bar 50 with a lug 66 is selected and shifted toward the rear to perform its respective function.

7 Finally in the cycle, the carriage return function operating bar 50a will be cammed out of the aligned notches 122 (FIGURE 12) of the function code bars 46 by the function cam bar 48, all stop bars 28 and all function bars 58 being ca-mmed slightly away from the edges of the respective code rings 31 and code bars 46 just prior to the end of a cycle of operation. The machine is again in a neutral or idle condition, ready to receive the next incoming code signal.

Modified function mechanism An alternate arrangement of the mechanism for moving the function operating bars 50 (shown in FIGURES 9 and 10) will now be described. In this version the function cam bar 48 has been eliminated and in lieu thereof, a small angular bracket 290 is attached to the bail 56' and performs the same function, that of cammin-g the function operating bars 50' away from the function code bars 46,

FIGURE 9 shows the slightly modified operating bars 50' in a neutral or unselected position. When the function code bars 46 are set for the selected function, the appropriate function operating bars 50' .will drop into the aligned notches of the function code bars 46 as soon as the function bail 56' moves toward the rear enough to allow the angular bracket 290 to ride into the inclined deep notch 292 of cut out 54 (see FIGURE 10). When this occurs, the associated bias spring 63 forces the selected function operating bar 50' to bottom in the aligned code bar notches, shifting the edge 294 of cut-out 54 into an interference condition with the path of movement of leading edge 57 of bail 56 and as the bail 56' moves farther to the right, edge 57' hit-s surface 294 mov' ing the operating bar 50' to the rear and, through appro priate linkage (as has been described), accomplishing the selected function. When the bail 56 moves back to the left on its return stroke to the neutral position, the angul-ar bracket 290 hits the inclined surface 295 of the notch 292 and came the selected function operating bar 50' out of the aligned notches .of the function code bars 46 thus accomplishing resetting of the function select-ing mechanism. The machine is now ready for the next signal.

Ink ribbon mechanism Referring to FIGURES l and 8, the ink ribbon 300 is carried on two spools 302 and 394 and extends across the front of the machine along appropriate guides and rollers which, for clarity of illustration, are not shown. However, two bent wire ribbon guides 306 (FIGURES 1 and carried by the print hammer assembly 24, cradle the ribbon as it passes immediately in front of the print hammer. These guides 306 traverse and move fore and aft with the print hammer and pull the ribbon 300 back away from the paper after each print stroke.

The ribbon operating mechanism derives power from the function cam 62 on camshaft 76 through the medium of a follower lever 308. A forked end 310 of follower iever 308 fits over a pin 312 on one arm 314 of a triple lever 316 and as the follower lever 308 oscillates during a cycle of camshaft rotation it transmits an oscillating motion to the lever 316. Pivotally carried on another arm 318 of lever 316 is a pawl 329 which, biased by a I4 spring 322, maintains engagement of its single tooth 324 with a ratchet 326. The pawl tooth 324 rides over the ratchet teeth on the upstroke and catches on the downstroke thus rotating the ratchet 326. The ratchet 326 is attached to an axially shift-able and rotatably mounted shaft 328 to which two gears 330 and 332 (see FIGURE 1) are attached, the gears 33% and 332 respectively meshing (one at a time) with two larger gears 334 and 336. The larger gears 334 and 336 are non-rotatably fastened to respective vertically mounted spool spindles 338 and 349. The spindles are rotatably mounted in a conventional manner on the machine frame. Ribbon spools 362 and 304 are interlocked to rotate with their respective spindles and the spindle which at a given time has its gear 334 (or 336) meshed with small gear 330 (or 332) drives its spool and winds the ink ribbon 3630 in one direction until it is exhausted from the other spool, at which time, the shaft 328 will be automatically axially shifted to disengage the gears to the winding spindle and engage the gears for the other spindle which reverses the direction of ribbon feed, Reversing of the ink ribbon 300 can be handled by any well'known means, a [common method using two small lugs built into the ends of the ink ribbon 300, each lug tripping a reversing mechanism to shift the shaft 328 to drive one or the other spool when either spool becomes nearly unwound. Due to such methods being well known, none will be described.

Typebar printer embodiment The heretofore described mechanism for a typewheel page printer can, with slight modification, be adapted to the operation of a typebar page printer. A typebar mechanism for use in combination with the operating mechanism herein described is referred to in the following des-cription, is shown in part in FIGURE 7, and is fully disclosed in the aforenoted K'leinschirndt Patent No. 2,- 773,931.

The code cage 40, as has been described for the printer 20, is positioned at the end of the square shaft 350 and initiation of signals can be made through either a keyboard similar to that shown in Kleinschmidt Patent No. 2,776,961 or through a pre-punched tape which is fed through a tape reader associated with the printer. The code characters on the tape are sensed and then relayed in parallel to the solenoids for the code cage 40.

Instead of a rotationally positionable typewheel 22 there will be a travelling carriage typebasket of which one typebar 352 is shown in FIGURE 7. Each of the typebars :352 carry a letterlor figure which corresponds to the multiple stop bars 28 and the function bars 50 in the code cage 40. The typebar printer square shaft 350 rotates as does the aforedescribed typewheel printer square shaft 26 and attached thereto and axially shiftable therealong is a gear 354 which is meshed with a second gear 356.

The second gear 356 is attached to a hollow shaft 358 and attached to the opposite end of hollow shaft 358 is a forked bracket 360 which is interlocked with a double fingered bracket 362. Bracket 362 is attached to the end of a smaller shaft 364 which slides inside hollow shaft 358. On the opposite end of the small shaft 364 is a grooved collar 366 and fitting into its groove loosely (to allow a free pivotal action as well as a sliding movement) is a bail 368.

When a selection is made, the code cage stop bar 28 'for that selected character is moved into place, blocking the stop arm 30 which, being directly attached to square shaft 350 causes it to also stop rotating (see FIGURE 5). When square shaft 350 is caused to stop rotating, hollow shaft 358, of course, ceases to rotate as does the forked bracket 360 and the double fingered bracket 362. Finger 370 is now in alignment with a desired selected push bar 372. An instant later the'bail 368 is actuated, moving coaxial shaft 364 forward, causing it to slide inside of hollow shaft 358. This causes the double fingered bracket 362 to move forward sharply,

t A3 fingers 370 and 370 being guided by ends 374 and 374' of the forked bracket 360 and when this occurs finger 370 strikes the end 376 of the selected push bar 372. Push bar 372 moves forward and its geared end 378, being meshed with the geared end 380 of the typebar 352 causes the typebar 352 to swing upward sharply until the type pallet 382 hits the ribbon end paper against platen 384 printing the selected character.

The code cage 40 is then set up to select the next incoming code character and the cycle is repeated.

Any number of additional functions such as a signal bell function, :a starting function for an answering or return message device or a function for controlling other allied equipment can be added when desired by merely adding additional function bars to the machine (as shown in phantom in FIGURE 13).

The balance of the mechanical and functional operating features of the typebar printer herein described can, with only slight modification, be identical to the mechanism previously described relative to the miniature typewheel bulletin printer.

The invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.

What is claimed and desired to be secured by United States Letters Patent is:

1. A printing telegraph receiver comprising: a movable type carriage; a rotatable positioning shaft; a type character selection device mounted on said movable carriage and slidably drive connected to said positioning shaft for longitudinal movement relative thereto and conjoint rotation therewith; means responsive to a code signal combination representative of a character to be printed to selectively position said shaft whereby said device is positioned for selection of a particular type character to be printed; means to cause said selected type character to be printed on a record medium; means to select and accomplish at least the machine functions of carriage return and line pace and Letters and Figures shift of said carriage; said selecting means including two-position selection code members and operative shift bars selected by permutative positioning of said code members from a home position; and means adapted to connect to and ensure placement of all said code members and said selected bars to said home position prior to the start of each receiver cycle.

2. A printing telegraph receiver comprising: a movable type carriage; a rotatable positioning shaft; a type character selection device mounted on said movable carriage and slidably drive connected to said positioning shaft for longitudinal movement relative thereto and conjoint rotation therewith; means responsive to a code signal combination respresentative of a character to be printed to selectively position said shaft whereby said device is positioned for selection of a particular type character to be printed; means to cause said selected type character to be printed on a record medium; means to select and accomplish at least the machine functions of carriage return and line space and Letters and Figures shift of said carriage; said selecting means comprising a group of twoposition individual notched permutation segments constituting selection code members and enabling in combination a plurality of selective rows of notches and a plurality of said operative shift bars, each'of which is associated with a respective selected row of notches and is selected by permutative positioning of said code members from a home position, means for simultaneously permutatively positioning each of said individual segments in one of its two positions to align one row of notches, a rotatable stop arm directed rotatable with said positioning shaft, means to shift the bar associated with a selected and aligned row of notches into said aligned row of notches whereby a part of said bar is projected into the path of said rotatable stop arm, a projection on said stop arm to engage the projected bar, and means structurally independent of said code segments to cyclically move and maintain said bars out of engagement with said segments during selective permutative positioning of individual segments; and adapted to connect to and ensure placement of all said code members and said selected bars to said home position prior to the start of each receiver cycle.

3. A printing telegraph receiver as defined in claim 2, wherein said individual notched segments are a plurality of coaxial side by side code disks with notched peripheries, said bars are arranged circumferentially around the'code disk peripheries and resiliently biased toward engagement with said code disks, and said means to cyclically move and maintain said bars out of engagement with the code disks includes a multiple cam disk coaxial with said code disks including a plurality of inclined cam rises at least equal in number to said bars and adapted to engage and force said bars radially outwardly away from said code disks upon angular shift of said cam disk.

4. A printing telegraph receiver as defined in claim 2, wherein said individual notched segments are parallel, lineally shiftable, side by side code bars with notched edges; said shift bars are arranged substantially normal to and biased toward engagement with the notched edges of said code bars; and said means to cyclically move and maintain said bars out of engagement with the code disks includes a multiple cam bar mounted for parallel shifting relative to and beside said code bars, having a plurality of inclined cam rises at least equal in number to said shift bars and adapted to engage and force said shift bars away from said code bars upon lineal shifting of said cam bar.

5. A printing telegraph receiver comprising: a movable type carriage; a rotatable positioning shaft; '21 character selection device mounted on said movable carriage and slidably drive connected to said positioning shaft for longitudinal movement relative thereto and conjoint rotation therewith; means including two-position selection code members and operative shift bars selected by permutative positioning of said code members from a home position responsive to a code signal combination representative of a character to be printed to selectively position said shaft whereby said device is positioned for selection of a particular type character to be printed; means to print said selected type character on a record; and means adapted to connect to and ensure placement of all said code members and said selected bars to said home position prior to the start of each receiver operating cycle.

6. A printing telegraph receiver as defined in claim 5, wherein said type carriage is a typebar basket with plural operable typebars and said character selection device is a rotatable spider adapted to select a desired typebar and be shifted to actuate said selected typebar through a printing stroke by said print means.

7. A printing telegraph receiver as defined in claim 5, wherein said type carriage is a typewheel carriage carrying a typewheel, said character selection device comprises a typewheel hub slidably drive connected to said positioning shaft, and said print means includes a print hammer aligned with and shiftable with the typewheel.

8. A printing telegraph receiver comprising: a movable carriage with plural type character means; a rotatable positioning shaft; a type character selection device mounted on said movable carriage slidably drive connected to said positioning shaft for longitudinal movement relative thereto and conjoint rotation therewith; means including selection locking code members and stop bars positioned from a non-selected and unlocked position said shaft whereby said device is positioned for selection of a particular type character to be printed; means to print said selected type character on a record; means adapted to connect to and ensure placement of all code members and stop bars to said non-selected and unlocked home position prior to receiving a code signal; and power means connected to operate said receiver through a cycle in response to each received code signal combination.

9. A printing telegraph receiver comprising: a stationary selector mechanism including a rotatable first shaft projecting rearwardly of the receiver, and a selectively positionable stop arm secured for rotation there- .with adapted to receive and convert permutative groups .of electrical signals into mechanical movement; a rotatable second shaft directly and positively drive connected .to and disposed normal to said first shaft, selectively positioned by selective positioning of said stop arm in said selector mechanism; a carriage support bar; recording means including type printing carriage means carrying a plurality of character type faces and means for accomplishing printing thereby; means supporting said carriage means for reciprocable movement on said support bar and on said rotatable second shaft; means on said carriage means coacting with said rotatable second shaft to select a particular type face corresponding to a received group of signals and in accord with selective position of said shaft; power means to furnish rotation to said shafts;

and means to actuate the means for accomplishing printing of the selected character on a page subsequent to selective positioning of said stop arm.

10. A printing telegraph receiver as defined in claim 9, wherein said power means comprises a rotatable electric motor rearwardly of. said second shaft having its shaft parallel to said first rotatable shaft, connection means including a function operating cam shaft and a slip coupling providing a drive connection between said motor and said second rotatable shaft, and means to actuate the printing means including a cam on said cam shaft.

11. A printing telegraph receiver comprising: a rotatable function cam shaft; a selecting shaft frictionally rotated by said function shaft; means for initiating function shaft rotation and automatically stopping rotation after a predetermined cycle of angular rotation; means controlled by function shaft angular position for enabling selective starting and stopping of rotation of said selecting shaft at any one of a plurality of distinct angular positions, corresponding to a plurality of respective code signals, within a predetermined increment of said function shaft cyclic angular rotation, said predetermined incrementof function shaft cyclic rotation being always preceded by another predetermined increment of function shaft rotation with the same said cyclic rotation; and

means engaging said function shaft for enabling power operation of machine functions during function shaft rotation after said predetermined increment.

12. A printing telegraph receiver as defined in claim 11, wherein said means controlled by function shaft angular position for enabling selective stopping of rotation of said selecting shaft includes a selector mechanism with two-position code members and selected shift bars, shiftable means to shift and maintain said selector mechanism in an inoperative home position, and a mechanism connected to and operated by said cam shaft during its initial rotation to move said shiftable means tora' position releasing said selector mechanism to thereafter accomplish its selective operation.

13. A printing telegraph receiver as defined in claim 11, wherein the means engaging said function shaft for enabling power operation of machine functions includes reciprocable means for at least actuating line feed and said means for selectively stopping rotation of said selecting shaft includes means selected thereby for engagement by said reciprocable means to determine operation of said named functions.

14. A printing telegraph receiver comprising: a rotata- -ble selecting shaft; means for initiating shaft rotation;

said code members to control operation of machine mechanism in accord with the received coded signal combination; means responsive to the coded signal combination to permutatively hold said selected code members in their other positions; and a reset device for placing all code members in said other position until said code signal combination is received by said holding means and including a part rotatably synchronized with shaft rotation.

15. A printing telegraph receiver comprising: a rotatable selecting shaft; means for initiating shaft rotation; means for stopping rotation of said shaft at selected position in accordance with receipt in the printer of a coded signal combination including notched two-position coaxial code disks resiliently biased to one of their posiacter print positions of said selecting shaft in accord with the received coded signal combination; means responsive to the coded signal combination to permutatively hold said selected code disks in their other positions; and a reset device for positively pivoting all code disks about their axis to said other position and maintaining all disks in such other position until said code signal combination is received by said holding means and including a part rotatably synchronized with shaft rotation.

16. A printing telegraph receiver for receiving coded electrical signal combinations and recording character representations of the code signal combination received comprising: a selector mechanism, including a unidirectional, motor driven, rotary selection shaft, adapted to convert received electrical signal combinations into mechanical movement; recording means including movable carriage means; means, including a unidirectionally rotated type drum, carried by said carriage means and conwith a received signal combination; a cable rigging means spring loaded at one end and connectable through a controlled drive pulley to a power source for normally moving said carriage means one character space for each recording operation and upon controlled release of said drive pulley for returning said carrage means to starting position under spring loaded force; a first means operable on said cable rigging independently of said drive pulley for providing an operational space shifting and locking of said carriage means apart from the character spacing action whereby the means to record a specific character carried by said carriage means and controlled by said selector mechanism will record a different specific character of the selected group of characters in accord with the .same received code signal combination; and a second means for unlocking said first means subsequent to a lockingvaction and including part of said first means for providing operational space shifting in a direction opposite to shift accomplished by said first means.

17. A telegraph page printer comprising: selecting means including a rotatable selecting shaft; a typewheel mounted on said shaft for rotation with said shaft and slidable axially thereon; a pivotable print hammer shaft disposed parallel to said selecting shaft; a print hammer fixed for pivotal movement with said print hammer shaft and axially movable thereon; means for pivoting said print hammer shaft to initiate a print operation; a cable rigging including at least two stretches of cable substantially parallel with respective ones of said shafts and shiftable in the same direction; a multiple pulley means with a ratchet wheel secured thereto; cyclically driven pawl means cooperating to drive said ratchet for incrementally shifting both of said cable stretches to simultaneously shift said typewheel and print hammer in synchronism, step by step from one side of the page printer to the other side; and means including a detent for said ratchet for shifting said cable in the opposite direction to shift said typewheel and print hammer back to said one side; said selecting means including a code barmechanism with solenoids for receiving code signal combinations and innected to said selecting means, is subject to selection operation conjointly therewith and includes selectively operable function operating means cyclically operable when selected during a machine operating cycle to perform a selected machine function.

19. A printer as defined in claim 18, wherein said function operating means includes means adapted to in- 'terfere with said means for pivoting said print hammer shaft upon initiation of each machine cyclic operation calling for selection of a machine function to provide means for preventing a print function whenever said se- 'lected function operating means is being cyclically operated.

20. A printer as defined in claim 17, wherein said hammer is positioned in front of the typewheel; an ink ribbon and a record page is disposed between the ham- -mer and typewheel; a cradle device is secured on said hammer and freely engages said ribbon forward of and at both sides of said hammer to maintain said ribbon in front of said hammer as said hammer shifts across the record page and to pull the ink ribbon back from the record page during the return stroke of the print hammer.

21. A telegraph page printer comprising: selecting means including a rotatable selecting shaft; a typewheel mounted on said shaft for rotation with said shaft and slidable axially thereon; a pivotable print hammer shaft disposed parallel to said selecting shaft; a print hammer fixed for pivotal movement with said print hammer shaft and axially movable thereon; means for pivoting said print hammer shaft to initiate a print operation; a cable rigging including at least two stretches of cable substantially parallel with respective ones of said shafts and shiftable in the same direction; a multiple pulley means with a ratchet wheel secured thereto; cyclically driven pawl means cooperating to drive said ratchet for incrementally shifting both of said cable stretches to simultaneously shift said typewheel and print hammer in synchronism, step by step from one side ofuthe page printer to the other side; means including a detent for said ratchet for shifting said cable in the opposite direction to shift said typewheel and print hammer back to said one side; said selecting means including a code bar 'mechanism with solenoids for receiving code signal combinations and including stop means for stopping said typewheel shaft at any of a plurality of angular positions in accord with the received signal; and an independent assembly of function selecting means, connected to said selecting means and subjectuto selection whenever said selected function operating means is be- 20 ing cyclically operated: said means for preventing a print function further comprising a print hammer operating lever having a latching lug, a print hammer blocking lever with a hooked end fixed for pivotal movement with said lug on said print hammer operating lever, and a lug on each function operating means operatively disposed relative to said blocking lever for engagement with said blocking lever after selection of and initiation of each function operation; said print hammer operating lever when engaged by said blocking lever preventing printing movement of said print hammer shaft during 'the cycle of operation and being operable to release said blocking lever at termination of the cycle of operation.

22. A telegraph page printer receiver comprising: a rotatable typewheel shaft; a plural row typewheel mounted on said shaft for rotation with said shaft and slidable axially thereon; a pivotable print hammer shaft disposed parallel to said typewheel shaft; a print hammer fixed for pivotal movement with said print hammer shaft and axially movable thereon; a double sheave cable pulley; a cable rigging including said pulley and at least two independent stretches of cable substantially parallel with said shafts and shiftable in the same direction upon rotation of said pulley; means for incrementally rotating said pulley in one direction to simultaneously shift said typewheel and print hammer in synchronism for step by step character spacing from one side of the page printer to the other side; means for shifting said cable stretches in the opposite direction to shift said typewheel and print hammer back to said one side; means including a portion of said rigging operable on only one of said cable stretches for shifting said stretch independently of stepping by said pulley to shift the relative positions of said typewheel and said print hammer so a'different row of type will be in print position adjacent the hammer; means for automatically maintaining said cable stretch in shifted position; and means including said last named means for shifting said cable stretch back to its original position relative to the other cable stretch.

23. A page printer comprising: a character selector 'mechanism including rotatable selecting shaft means; a function selector mechanism including a rotatable cam adjacent each other with the motor shaft and the seshaft; an electric motor with a rotatable output shaft; said selector mechanisms and said motor being disposed lecting shaft substantially parallel; selective clutching -means for drive connecting said motor shaft to said 'cycle of angular rotation of said cam shaft; slip coupling means drive connecting said cam shaft to said selecting shaft means and providing a step-up speed ratio between said cam shaft and said selecting shaft means;

said selector mechanisms including a plurality of solenoids for receiving electrical code signal combinations in simultaneous form resulting in permutated arrangement of energized and de-energized ones of said solenoids, a code disk cage surrounding part of said selecting shaft means, a plurality of notched, two-position code disks and a multiple cam, reset disk coaxially mounted in said code cage about the axis of said part of said selecting shaft means; a plurality of print character representative stop bars mounted in said cage around the periphery of said notched code disks and said cam disk, means individually biasing said stop bars inwardly towards a drop position in a respective associated row of code disk notches, only one row of notches being aligned in accord with each. permutative positioning of said code disk, and all of said stop bars being engageable and maintained against their biased said cam disk is in its other position, and a stop arm se- 21 cured on said part of said selecting shaft means with a projection rotatably adjacent said stop bars and engageable with any dropped stop bar to stop rotation of said selecting shaft means at a predetermined angular position corresponding to the selected stop bar; character printing means connected to said selecting shaft including a plurality of print face means corresponding to the number of stop bars and which are selectable for printing in accord with the angullar position of said selecting shaft; mechanism including a portion of and responsive to cyclic rotation of said function shaft for operating said character printing means through a print cycle subsequent to engagement of said stop arm with a selected and dropped stop bar; mechanism including a portion of and responsive to cyclic rotation of said function shaft for letter spacing; said function selector mechanism including a reciprocable bail cyclically operated by said function shaft, a plurality of resiliently biased function operating bars adapted to be shifted into interlocked engagement with said function bail and thereafter be positively moved by reciprocation of said function bail, a plurality of twoposition notched function code bars adjacent said function operating bars and permitting shifting of selected ones of said function operating bars into associated aligned rows of notches depending upon permutative positioning of said code bars; cam means movable to one position to cyclically move and maintain said function operating bars away from said code bars until selective positioning of said code bars has occurred; a plurality of machine function mechanisms connected respectively to and for operation by individual ones of said function operating bars; and connecting means between sets consisting of one of said solenoids, one of said code disks and one of said code bars to enable simultaneous positioning of related code disks, code bars and solenoids; said solenoids being spring biased away from energized position; means responsive to a received signal for actuating said clutch to start a cycle of function shaft rotation; mechanism, including said function shaft, cyclically operable in conjunction with movement of said cam disk to said one position and of said cam means to said one position to positively set and maintain all solenoids to operative position prior to their being energized in accord With'the received signal and also, in conjunction with movement of said cam disk to said other position and of said cam means away from said one position, to release set control of said solenoids while such solenoids are energized.

24. In a selector mechanism for a printing telegraph receiver, a group of two-position individual notched permutation segments having in selective combination a plurality of different rows of notches; a signal representative bar member associated with said row of notches; means for simultaneously permutatively positioning each of said individual segments in one of its two positions to align one row of notches; a cyclically operable power driven member; means to move the bar member associated with said aligned row of notches into said aligned row of notches whereby said bar member is projected into the path of said cyclically operated power driven member; a projection on said power driven member to engage the projected bar member and thereby enable a machine operation; and means structurally separate from said segments to cyclically move and maintain said bar member out of engagement with said segments during positioning of individual segments.

25. In a selector mechanism for a printing telegraph receiver, a group of two-position individual notched permutation code disks having in selective combination a plurality of rows of notches; a signal representative bar member associated each said row of notches; means for simultaneously permutatively positioning each of said individual code disks in one of its 'two positions to align one row of notches; a rotatable stop arm; means to move the bar member associated with said aligned row of notches into said aligned row of notches whereby said bar member is projected into the path of said rotatable stop arm; a projection on said stop arm to engage the projected bar members; and means including a cam disk engageable with all bar members to cyclically move and maintain said bar member out of engagement with said code disks during positioning of individual segments.

26. A selector mechanism including: a rotatable shaft adapted to be selectively positioned; a group of twoposition code disks each having a plurality of notches circumferentially located around its periphery; a code disk cage; stop bars arranged in said cage concentrically about said disks; a stop arm secured to said rotatable shaft; means for permutatively positioning said code disks to align one row of notches to permit one of said stop bars to enter said aligned row and be projected in the path of said stop arm; said last named means in: cluding power means to cyclically engage andposition all of said disks to one common position and then release positional control of said disks; code combination signal receiving means responsive to receipt of a code combination signal, including a device in control engagement with said power means and a plurality of selective control devices individually connected to said disks, to initiate one cycle of said power means, maintain selected ones of said disks in said one position in accord with the received code combination signal and permit any non-selected disk to shift to the other of said two positions; and means, subject to being rendered ineffective by selected control devices in accord with a received code combination signal, connected to bias all said disks to said other positions.

27. In a selector mechanism: a signal controlled, cyclically rotated shaft; a selecting shaft, adapted to be selectively positioned; slip coupling means to drive said selecting shaft as said cyclically rotated shaft rotates; a stop members secured tov said selecting shaft and rotatable therewith, said member having an engageable arm; selectable means movable into the path of said arm to abruptly engage said arm at any selected angular position of a plurality of positions during each revolution of said function shaft to selectively position said -selecting shaft each time said arm is engaged; and a spring leaf latch means on said arm cooperating with said engaging means engagement of the arm therewith to automatically lock said arm and said selected engaging means together to positively prevent rebound of said arm upon such abrupt engagement.

28. In combination With a code receiving selector mechanism including a plurality of shiftable code members, a rockable code member reset cam segment adapted upon being rocked to engage and place all code mem bers in a non-operative position, said reset cam having an arcuate edge and comprising a flat substantially diskshaped segment including a substantially concentric aperture, a plurality of circumferentially equidistantly spaced inclined cam surfaces each of which is associated with and adapted to engage a specific one of said code members upon rocking of said reset member, and connecting -means for an operating member.

29. In a selector mechanism as defined in claim 24, wherein said means to cyclically move and maintain said bar member out of engagement with said segments comprises cooperative reset camming means including a portion of all said bar members and a cyclically positively shiftable power operated means adapted to engage and disengage said portions on all of said bars during its cyclic shifting movement.

30. In a selector mechanism as defined in claim 29, said notched segments are lineally shiftable parallel members notched along similarly disposed parallel edges, means mount said bar members normal to the notched edges of said segments for a compound shifting movement toward said notched segments and also along the associated row of notches, each said bar member includes an abutment projected into the path of movement of said projection on said power drive member upon selection of said bar member by permutative positioning of said notched segments, and said power driven member is positively driven through its cycle to result in engagement between its projection and said abutment to provide shifting movement of said selected bar member along the associated row of notches.

31. In a selector mechanism as defined in claim 29, said power operated means portion of said reset camming means being a physical separate mechanism and being cyclically shiftable in a distinctly separate path from said power driven member.

32. In a selector mechanism as defined in claim 31, said power operated means portion of said reset camming means comprising a cam bar shiftably mounted adjacent and parallel to said notched segments and having a plurality of cam rises on one edge thereof each of which is adapted to engage a portion of an associated bar member upon cyclic power operated shifting of said cam bar and force said bar members away from the notched edges of said notched segments.

33. In a selector mechanism as defined in claim 29, means rigidly securingsaid power operated means portion of said reset camming means to said power driven member whereby it is cyclically shiftable in a similar path to and simultaneously with the cyclic path of movement of said power driven member.

34. In a selector mechanism as defined in claim 33, said bar member portions of said reset camming means are inclined notches located in aligned relationship in similar edges of said bar member, and said power operated means portion of said reset camming means is a cam plate shiftable with said cyclically operated power driven member to engage an inclined edge of all said inclined notches as said cyclically operated power driven member terminates its operated cycle and approaches the start position for a subsequent operational cycle, to thereby cam all bar members away from the notched edges of said notched segments.

35. In a selector mechanism for a printing telegraph receiver, a cyclically operable power driven member; a group of two-position individual notched permutation segments having in selective combination a plurality of different rows of notches; a signal representative bar member associated with each said row of notches; means for simultaneously permutatively positioning each of said individual segments in one of its two positions to align one row of notches; means to move the bar member associa-ted with said aligned row of notches into said aligned row of notches whereby said bar member is projected into the path of said cyclically operated power driven member; a projection on said power driven member to engage the projected bar member and thereby enable a machine operation; reset means structurally separate from said segments to cyclically move and maintain said bar members out of engagement with said segments during a positioning shift of individual segments and .then permit engagement of said bar members with said segments; said means for permutatively positioning said segments comprising power means to cyclically engage and position all of said notched segments to one common position and then release positional control of said disks, code combination signal receiving means responsive to receipt of a code combination signal to initiate one cycle of said power means, to maintain selected ones of said notched in, the notches in said segments are square notches and the movement of a selected bar member into an associated aligned row of notches automatically interlocks all segments against any further repositioning until said selected bar member is moved away from said segments during cyclic operation of said reset means.

37. A selector mechanism as defined in claim 35 wherein, said code combination signal receiving means includes a plurality of selector solenoids, one for each of said notched segments, a plurality of means operatively connecting the armatures of individual ones of said solenoids to individual associated ones of said notched segments so that energization of any solenoid will cause its armature to urge said associated notched segment to its said one position, and a power operated bail means, common to all of said means connecting said armatures to said segments, adapted to engage said connecting means and positively shift all armatures with associated notched segments to said one position; and said means subject to overcontrol by said signal receiving means comprises a plurality of spring means individual to each solenoid and segment set connected to bias said armatures away from energized position toward the said other positions of said segments.

38. A selector mechanism as defined in claim 37 wherein, means are provided in engagement with and operatively coordinate the cyclic operation of said reset means and said segment positioning power means so that the portion of cyclic operation of said segment positioning means which enables positioning of all segments to said one position overlaps the portion of cyclic operation of said reset means which moves and maintains said bar members out of engagement with said segments.

39. A selector mechanism as defined in claim 38 wherein, said coordinating means is a rotatable cam, each of said reset means and said segment positioning means include a cam follower riding on said rotatable cam and said segment positioning means includes resilient lost motion linkage means between its cam follower and said bail to enable initiation of segment positioning cam follower action, without conjoint movement of said segments, prior to movement of said selected bar out of said aligned row of notches by said reset means.

at). A selector mechanism as defined in claim 37, where- --in each of said means connecting a solenoid armature to its associated segment comprises a resiliently biased lost .rnotion means permitting said connection and said segment to be over-positioned by said power operated bail beyond the energized solenoid position of said armature.

41. A printing telegraph receiver including a selector mechanism rendered operative in response to received code signal combinations and a plurality of means controlled by said selector mechanism to enable receiver operations, said selector mechanism comprising: a first selecting means to select and enable actuation of at least a portion of said plurality of receiver operation enabling means; a second selecting means physically separate from said first selecting means to select and enable actuation of at least a second portion of said plurality of receiver operation enabling means; and means interconnecting and enabling correlated operation of both of said selecting 'means responsive to receipt of any code signal combination.

42. A printing telegraph receiver comprising: a movable type carriage; a character selection device mounted be printed on a record medium; a second selecting means spaced from first selecting means and responsive to code signal combinations representative of at least the machine functions of carriage return, Letters shift and Figures shift of said carriage to select and enable the desired machine function; and means interconnecting and enabling 25 correlated operation of both of said selecting means responsive to receipt of any code signal combination.

43. A printing telegraph receiver comprising: a movable type carriage; a rotatable positioning shaft; a character selection device mounted on said movable carriage and connected to said positioning shaft for conjoint rotation therewith and selective positioning thereby; a first selecting means responsibe to a code signal combination representative of a character to be printed to selectively position said shaft whereby said selection device is positioned for selection of a particular type character to b printed; means to cause said selected type character to be printed on a record medium; a second selecting means spaced from said first selecting means to select and accomplish at least the machine functions of carriage return, Letters shift and Figures shift of said carriage; both of said first and said second selecting means including a group of two-position selection code members and associated operative shift bars selected by permutative positioning of said code members; and means interconnecting corresponding ones of both of said groups of code members enabling correlated permutative positioning of all of said code members.

44. A printing telegraph receiver comprising: a movable type carriage; a character selection device mounted on said movable carriage for selective positioning thereon; a first selecting means including a first group of twoposition selection code members and a first group of associated operative shift bars selected by permutative positioning of said code members to selectively position said selection device for selection of a particular type character to be printed; means operatively coordinated with said first selecting means to print said selected type character on a record; a second selecting means including a second group of two-position selection code members and a second group of associated operative shift bars selected by permutative positioning of said second group of code members; means operatively coordinated with said second group of shift bars for enabling receiver functions subsequent to selection of any of said second group of shift bars; and means responsive to receipt of a code signal combination to enable conjoint permutative positioning of said group of code members.

4-5. A printing telegraph receiver as .claimed in claim 44, wherein blocking means are provided to be operatively shifted to engage and block operation of said means to print a selected type character; and means, rendered operative subsequent to selection of a one of said second group of shift bars are provided for engaging and operatively shifting said blocking means to print blocking position.

46. A printing telegraph receiver comprising: a movable type carriage; a rotatable positioning shaft; a character selection device mounted on said movable carriage and connected to said positioning shaft for conjoint rotation therewith and selective positioning thereby; a first selecting means including a first group of two-position selection code members and a first group of associated operative shift bars selected by permutative positioning of said code members to selectively position said shaft whereby said selection device is positioned for selection of a particular type character to be printed; means operatively coordinated with said first selecting means to print and selected type character on a record; a second selecting means including a second group of two-position selection code members and. a second group of associated operative shift bars selected by permutative position of said second group of code members; means operatively coordinated with said second group of shift bars for enabling receiver functions subsequent to shift bar selection; and means responsive to receipt of a code signal combination to enable conjoint permutative positioning of both of sat-d groups of code members.

47. A printer as defined in claim 5 wherein an independent assembly of function selecting means is connected to said selecting means, is subject to selection operation conjointly therewith and includes selectively operable function operating means cyclically operable when selected during a machine operating cycle to perform a selected machine function.

48. A printer as defined in claim 47 wherein said function operating means include means adapted to interfere with said means to print said selected type character upon initiation of each machine cycle operation calling for selection of a machine function to provide means for preventing a print function whenever said selected function operating means is being cyclically operated.

49. In a selector mechanism for a printing telegraph receiver, a first group of two-position individual notched permutation segments having in selective combination a plurality of different rows of notches; a first pulrality of signal representative bar members, one being associated with each said row of notches; means for simultaneously permutatively positioning each of said individual segments in one of its two positions to align one row of notches; a first cyclically operable power driven member; means to move the bar member associated with said aligned row of notches of said first group of segments into said aligned row of notches whereby said bar member is projected into the path of said first cyclically operated power drive member; a projection on said first power driven member to engage the projected bar member and thereby enable a machine operation; a second group of two-position individual notched permutation segments separate and spaced from said first group of segments and having in selective combination a plurality of different rows of notches; a second plurality of signal representative bar members, one being associated with each said row of notches in said second group of segments; means enabling simultaneous permutative positioning of the segments in said second group of segments to align one row of notches operative by and in conjunction with said means for positioning said first group of segments; a second cyclically operable power driven member; means to move the bar member associated with said aligned row of notches of said second group of segments into said aligned row of notches whereby said bar member is projected into the path of said second power driven member; a projection on said second power driven member to engage the projected bar member associated with said second group of segments and thereby enable a machine operation distinct from said first mentioned machine operation; and means directly relating the cyclic operation of both said first and said second power driven members.

50. In a selector mechanism as claimed in claim 49, means structurally separate from said segments to cyclically move and maintain all of said bar members of both said groups of bar members out of engagement with said segments during positioning of individual segments.

References Cited by the Examiner UNITED STATES PATENTS 1,201,809 10/ 16 Dixon 17=829 2,134,722 11/38 Long et al 1782'8 2,247,408 7/41 Reiber 17 829 2,754,361 7/5 6 Kleinschmidt 178-3 3 2,773,931 12/56 Kleinschmidt et al 17823 2,774,816 12/56 Yost 178-29 2,942,065 6/ 60 Howard 17 8--25 NEIL C. READ, Primary Examiner.

ROBERT H. ROSE, Examiner.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3,201,514 August 17, 1965 Edward E. Kleinschmidt t a1 It is hereby certified that error appears in the above numbered patent requiring correction and that the said Letters Patent should read as corrected below.

Column 1, line 38, for "0" read of column 2, line 54, for "embdiment" read embodiment column 3, line 11, for "opearting" read operating column 13, line 52, for "came" read cams column 15, line 7, for "end" read and column 25, line 8, for "responsibe" read responsive column 26, line 18, for "pulrality" read plurality Signed and sealed this 12th day of April 1966.

SEAL) .ttest:

RNEST W. SWIDER EDWARD J. BRENNER ttesting Officer Commissioner of Patents 

1. A PRINTING TELEGRAPH RECEIVER COMPRISING: A MOVABLE TYPE CARRIAGE; A ROTATABLE POSITIONING SHAFT; A TYPE CHARACTER SELECTION DEVICE MOUNTED ON SAID MOVABLE CARRIAGE AND SLIDABLY DRIVE CONNECTED TO SAID POSITIONING SHAFT FOR LONGITUDINAL MOVEMENT RELATIVE THERETO AND CONJOINT ROTATION THEREWITH; MEANS RESPONSIVE TO A CODE SIGNAL COMBINATION REPRESENTATIVE OF A CHARACTER TO BE PRINTED TO SELECTIVELY POSITION SAID SHAFT WHEREBY SAID DEVICE IS POSITIONED FOR SELECTION OF A PARTICULAR TYPE CHARACTER TO BE PRINTED; MEANS TO CAUSE SAID SELECTED TYPE CHARACTER TO BE PRINTED ON A RECORD MEDIUM; MEANS TO SELECT AND ACCOMPLISH AT LEAST THE MACHINE FUNCTIONS OF CARRIAGE RETURN AND LINE SPACE AND LETTERS AND FIG- 